CA1121289A - Friction bevel coupling with double cones particularly for use in drive mechanisms of ships - Google Patents
Friction bevel coupling with double cones particularly for use in drive mechanisms of shipsInfo
- Publication number
- CA1121289A CA1121289A CA000347645A CA347645A CA1121289A CA 1121289 A CA1121289 A CA 1121289A CA 000347645 A CA000347645 A CA 000347645A CA 347645 A CA347645 A CA 347645A CA 1121289 A CA1121289 A CA 1121289A
- Authority
- CA
- Canada
- Prior art keywords
- coupling
- drive member
- annular pistons
- output shaft
- shaft
- Prior art date
- Legal status (The legal status is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the status listed.)
- Expired
Links
- 230000008878 coupling Effects 0.000 title claims abstract description 85
- 238000010168 coupling process Methods 0.000 title claims abstract description 85
- 238000005859 coupling reaction Methods 0.000 title claims abstract description 85
- 230000007246 mechanism Effects 0.000 title description 7
- 238000004140 cleaning Methods 0.000 claims description 2
- 239000003795 chemical substances by application Substances 0.000 description 8
- 230000005540 biological transmission Effects 0.000 description 5
- 238000010276 construction Methods 0.000 description 4
- 239000003921 oil Substances 0.000 description 4
- 229910000906 Bronze Inorganic materials 0.000 description 2
- 229910001018 Cast iron Inorganic materials 0.000 description 2
- 239000010974 bronze Substances 0.000 description 2
- KUNSUQLRTQLHQQ-UHFFFAOYSA-N copper tin Chemical compound [Cu].[Sn] KUNSUQLRTQLHQQ-UHFFFAOYSA-N 0.000 description 2
- 230000006870 function Effects 0.000 description 2
- 239000012535 impurity Substances 0.000 description 2
- 238000009434 installation Methods 0.000 description 2
- 239000000463 material Substances 0.000 description 2
- BSFODEXXVBBYOC-UHFFFAOYSA-N 8-[4-(dimethylamino)butan-2-ylamino]quinolin-6-ol Chemical compound C1=CN=C2C(NC(CCN(C)C)C)=CC(O)=CC2=C1 BSFODEXXVBBYOC-UHFFFAOYSA-N 0.000 description 1
- 239000002775 capsule Substances 0.000 description 1
- 239000010720 hydraulic oil Substances 0.000 description 1
- 238000005461 lubrication Methods 0.000 description 1
- 238000004519 manufacturing process Methods 0.000 description 1
- 239000002923 metal particle Substances 0.000 description 1
- 230000002265 prevention Effects 0.000 description 1
Classifications
-
- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
- F16D—COUPLINGS FOR TRANSMITTING ROTATION; CLUTCHES; BRAKES
- F16D13/00—Friction clutches
- F16D13/22—Friction clutches with axially-movable clutching members
- F16D13/24—Friction clutches with axially-movable clutching members with conical friction surfaces cone clutches
- F16D13/26—Friction clutches with axially-movable clutching members with conical friction surfaces cone clutches in which the or each axially-movable member is pressed exclusively against an axially-located member
-
- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
- F16D—COUPLINGS FOR TRANSMITTING ROTATION; CLUTCHES; BRAKES
- F16D25/00—Fluid-actuated clutches
- F16D25/06—Fluid-actuated clutches in which the fluid actuates a piston incorporated in, i.e. rotating with the clutch
- F16D25/062—Fluid-actuated clutches in which the fluid actuates a piston incorporated in, i.e. rotating with the clutch the clutch having friction surfaces
- F16D25/063—Fluid-actuated clutches in which the fluid actuates a piston incorporated in, i.e. rotating with the clutch the clutch having friction surfaces with clutch members exclusively moving axially
- F16D25/0632—Fluid-actuated clutches in which the fluid actuates a piston incorporated in, i.e. rotating with the clutch the clutch having friction surfaces with clutch members exclusively moving axially with conical friction surfaces, e.g. cone clutches
-
- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
- F16D—COUPLINGS FOR TRANSMITTING ROTATION; CLUTCHES; BRAKES
- F16D25/00—Fluid-actuated clutches
- F16D25/06—Fluid-actuated clutches in which the fluid actuates a piston incorporated in, i.e. rotating with the clutch
- F16D25/062—Fluid-actuated clutches in which the fluid actuates a piston incorporated in, i.e. rotating with the clutch the clutch having friction surfaces
- F16D25/063—Fluid-actuated clutches in which the fluid actuates a piston incorporated in, i.e. rotating with the clutch the clutch having friction surfaces with clutch members exclusively moving axially
- F16D25/0635—Fluid-actuated clutches in which the fluid actuates a piston incorporated in, i.e. rotating with the clutch the clutch having friction surfaces with clutch members exclusively moving axially with flat friction surfaces, e.g. discs
-
- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F02—COMBUSTION ENGINES; HOT-GAS OR COMBUSTION-PRODUCT ENGINE PLANTS
- F02B—INTERNAL-COMBUSTION PISTON ENGINES; COMBUSTION ENGINES IN GENERAL
- F02B61/00—Adaptations of engines for driving vehicles or for driving propellers; Combinations of engines with gearing
- F02B61/04—Adaptations of engines for driving vehicles or for driving propellers; Combinations of engines with gearing for driving propellers
- F02B61/045—Adaptations of engines for driving vehicles or for driving propellers; Combinations of engines with gearing for driving propellers for marine engines
Landscapes
- Engineering & Computer Science (AREA)
- General Engineering & Computer Science (AREA)
- Mechanical Engineering (AREA)
- Hydraulic Clutches, Magnetic Clutches, Fluid Clutches, And Fluid Joints (AREA)
- Mechanical Operated Clutches (AREA)
- Filtration Of Liquid (AREA)
- Mutual Connection Of Rods And Tubes (AREA)
- Retarders (AREA)
- Friction Gearing (AREA)
- General Details Of Gearings (AREA)
Abstract
ABSTRACT OF THE DISCLOSURE
The present invention provides a double-cone bevel coupling comprising a drive member provided with inner conical friction surfaces, an output shaft extending generally co-axially within said drive member, conical friction elements within said drive member having friction surfaces facing said inner conical friction surfaces of said drive member, annular pistons arranged generally concentrically with said output shaft and defining a space therebetween, said annular pistons being coupled to said output shaft by pivotal connections which allow the planes of said annular pistons to tilt rela-tive to said shaft while being constrained to rotate therewith said annular pistons being arranged to urge said friction elements into engagement with the drive member when pressuriz-ing agent is introduced into said space, and said output shaft being supported relative to said drive member by means of a bearing allowing tilting of the shaft relative thereto, whereby in the event of angular deviations of the output shaft, the annular pistons can tilt so that they remain correctly posi-tioned in said drive member.
The present invention provides a double-cone bevel coupling comprising a drive member provided with inner conical friction surfaces, an output shaft extending generally co-axially within said drive member, conical friction elements within said drive member having friction surfaces facing said inner conical friction surfaces of said drive member, annular pistons arranged generally concentrically with said output shaft and defining a space therebetween, said annular pistons being coupled to said output shaft by pivotal connections which allow the planes of said annular pistons to tilt rela-tive to said shaft while being constrained to rotate therewith said annular pistons being arranged to urge said friction elements into engagement with the drive member when pressuriz-ing agent is introduced into said space, and said output shaft being supported relative to said drive member by means of a bearing allowing tilting of the shaft relative thereto, whereby in the event of angular deviations of the output shaft, the annular pistons can tilt so that they remain correctly posi-tioned in said drive member.
Description
~lZlZ~9 ;
The present invention relates to a double-cone friction bevel coupling of the type which comprises an outer part having conical friction surfaces on its inner surfaces, and within said outer part, annular pistons coupled to an output shaft and asso-ciated with conical friction elements having friction surfaces on their outer surfaces arranged such that the coupling is engaged by pressurizing agent acting in a space between the annular -; pistons.
sevel couplings known so far comprise a fixed outer part -~10 and an axially moving inner part. In these couplings the axial movement of the inner part is carried out by means o~ gear and ;-ring wheel mechanism or by means of a multiple key slide system.
As a result no axial angle deviations have so far been permitted.
As, however, angular deviations always exist due to installation, -~ power transmission etc., thls often results in heavy wear in the slide system of the inner part of the coupling. Metal particles -produced by the wear often make the coupling jam and cause other ~ -~
kinds of trouble.
In known bevel couplings stringent requirements are made concerning the concentrity of the inner and outer parts of the coupling both during manufacture and installation of the coupling.
The eccentrity of the outer and inner parts results in losses ln the torque transmission capacity.
Another drawback of the prior art is imperfect operation in the vertical position.
, .
According to the present invention there is provided a -~
double-cone bevel coupling comprising a drive member provided with ;~
inner conical friction surfaces, an output shaft extending gener-ally co-axially within said drive member, conical friction elements within said drive member having friction surfaces facing said inner conical friction surfaces of said drive member, annular pistons arranged generally concentrically with said output shaft ' "
L28~
~ .
and defining a space therebetween, said annular pistons beirly coupled to said output shaft by pivotal connections which allow ~ the planes of said annular pistons to tilt relative to said shaft ;~ while being constrained to rotate therewith, said annular pistons :;"
C"j being arranged to urge said friction elements into engagement with .- ;
the drive member when pressurizing agent is introduced into said space, and said output shaft being supported relative to said " drive member by means of a bearing allowing tilting of the shaft relative thereto, whereby in the event of angular deviations ofthe -~ . . .
output shaft the annular pistons can tilt so that they remain correctly positioned in said drive member.
In a coupling in accordance with the invention, certain angle deviations in the shaft position are permitted, as the . ;::
~; coupling cones can freely take position relative to the outer part of the coupling due to a cardan joint that improves the contact between ~he coupling surfaces and consequently improves the torque transfer capacity.
Some eccentrity is also permitted as the bearing func-tions only as an axial bearing supporting the weight of inner parts of the coupling and the shaft when the coupling is disengaged.
;~
This bearing permits some radial movement. Hence the coupling cones can be centered relative to the outer parts of the coupling.
-:; .,.
As the coupling operates in horizontal position, the bearing ~` carries the radial loads caused by the inner parts of the coupling. ` `
~ , . , The bearing also prevents the coupling cones from touching the ~" outer parts of the coupling when the coupling is disengaged. i .
The coupling cones can be more easily made take position ;
; by means of cup springs than by means of helical springs. Space " can also be saved with using cup springs.
: : - ;, The coupling is functionally a dry type coupling, but -"~ when using hydraulic oil as the pressurizing agent for engaging ~` the coupling, advantages of a wet-type coupling can also be '.::
; - 2 - - ;;i `
~z~9 :
achieved, as coupling surfaces can be cleaned with the same oil by rinsing unfavourable impurities accumulated on the surfaces due to the centrifugal force. The cleaning of the coupling surfaces can be further improved by fitting the coupling cones with grooves.
; The cardan joint construction belonging to a coupling in accordance with the invention considerably reduces the amount . of impurities caused by wear.
The position of the coupling can also be freely chosen as it operates equally faultlessly in vertical and horizontal pOSitions and in all intermediate positions.
In order to avoid seizure, for instance bronze cast iron should preferably be sele~ted as the material of the coupling surfaces.
` A coupling in accordance with the invention can be made ~;
to operate as an overlaod protection clutch by limlting the maxi-mum pressure of the oil that engages the coupling by means of a system external to the coupling.
A coupling in accordance with the invention can favour--ably be positioned between two shaft ends or in such a way that both input and output shaft leave the coupling coaxially to the same direction.
The invention will now be described in more detail by way of example only, with reference to the accompanying drawings in which~
Figure 1 is a schematic illustration of a friction . ~ .
coupling in accordance with the invention, installed in the drive `
mechanism of a ship;
Figure 2 shows a cross sectional view of a coupling in accordance with the invention; and Figure 3 is an exploded view of the coupling shown in . ~
figure 2. ~ ~
. .:
The drive mechanism of the ship illustrated in fig. 1 .~
.
, comprises transmission equipment by means of which engine 36 drives propeiler 30. Starting from engine 36, the equipment comprises cardan shaft 33 that drives V-belt pulley 32. V-belt pulley 32 is connected with V-belts 31 to V-belt pulley 35 of the drive mechanism which V-belt pulley 35 drives bevel gear 25. Tubular shaft 24 is supported with bearings on frame 38 of the drive mech-anism and is equipped with bevel gear 26 driven by gear 25. At its top end, tubular shaft 24 is connected with outer parts 2 and 3 of the couble-cone coupling. The inner parts of the coupling ` 10 are connected by means of shaft 1, passing through tubular shaft ~;~
24, with bevel gear 27 which, via bevel gear 28 and its shaft 29 drives propeller 30 of the ship. The bottom part of the frame of drive mechanism 38 is made pivotable in the direction of arrow B
for steering the ship. ;
Figures 2 and 3 illustrate the detailed construction of ` the double-cone friction coupling.
Outer part 2,3 of the coupling is arranged to rotate within capsule 37 as engine 36 rotates. The inner parts of the ;;
coupling comprise a cardan joint 4 fastened to the top end of ` 20 shaft 1. Cardan joint 4 is fastened to the shaft by means of conical sleeve 5 and bolts 17. Cardan joint 4 also comprises pins 8, of which there are four located perpendicularly and radi- ~ -ally as shown in fig. 3. Over the pins 8 are slides 7 of square `~
cross-section. On both sides of a slide there are annular pistons 14 and 15 with forks 14' resp. 15', into which slides 7 of pins 8 ~' fit. The top annular piston 14 is loaded from above by two oppo-site cup springs 9, supported at their inner edges by means of ring 10. The bottom annular piston 15 is loaded by two opposite ;~
:` cup springs 11 supported by means of ring 10. In the inner circum- `
` 30 ference of annular pistons 14,15 there is a groove for O-ring 22 that seals the inside of annular pistons 14,15 against the . ~ .
cylindrical surface of part 4.
'~:
' ; , `'`'`
z~z~
The coupling comprises two opposite coupling cones 12 and 13. Cone 12 is fastened with bolts 19 to annular piston 15 and cone 13 is fastened with bolts 19 to annular piston 14.
; Between annular pistons 14 and 15 there is a space into which pressurized agent, preferably oil, can enter through channels 6 in shaft 1. Shaft l is supported by a special bearing 21 relative to outer part 2 of the coupling.
A feature of the bearing 21 is that it only works as an axial bearing carrying the weight of the inner parts of the coupling and the shaft when the coupling is disengaged. Bearing 21 however permits a radial or tilting movement of the shaft l.
As the coupling is disengaged, bearing 21 centers parts 3,13 and
The present invention relates to a double-cone friction bevel coupling of the type which comprises an outer part having conical friction surfaces on its inner surfaces, and within said outer part, annular pistons coupled to an output shaft and asso-ciated with conical friction elements having friction surfaces on their outer surfaces arranged such that the coupling is engaged by pressurizing agent acting in a space between the annular -; pistons.
sevel couplings known so far comprise a fixed outer part -~10 and an axially moving inner part. In these couplings the axial movement of the inner part is carried out by means o~ gear and ;-ring wheel mechanism or by means of a multiple key slide system.
As a result no axial angle deviations have so far been permitted.
As, however, angular deviations always exist due to installation, -~ power transmission etc., thls often results in heavy wear in the slide system of the inner part of the coupling. Metal particles -produced by the wear often make the coupling jam and cause other ~ -~
kinds of trouble.
In known bevel couplings stringent requirements are made concerning the concentrity of the inner and outer parts of the coupling both during manufacture and installation of the coupling.
The eccentrity of the outer and inner parts results in losses ln the torque transmission capacity.
Another drawback of the prior art is imperfect operation in the vertical position.
, .
According to the present invention there is provided a -~
double-cone bevel coupling comprising a drive member provided with ;~
inner conical friction surfaces, an output shaft extending gener-ally co-axially within said drive member, conical friction elements within said drive member having friction surfaces facing said inner conical friction surfaces of said drive member, annular pistons arranged generally concentrically with said output shaft ' "
L28~
~ .
and defining a space therebetween, said annular pistons beirly coupled to said output shaft by pivotal connections which allow ~ the planes of said annular pistons to tilt relative to said shaft ;~ while being constrained to rotate therewith, said annular pistons :;"
C"j being arranged to urge said friction elements into engagement with .- ;
the drive member when pressurizing agent is introduced into said space, and said output shaft being supported relative to said " drive member by means of a bearing allowing tilting of the shaft relative thereto, whereby in the event of angular deviations ofthe -~ . . .
output shaft the annular pistons can tilt so that they remain correctly positioned in said drive member.
In a coupling in accordance with the invention, certain angle deviations in the shaft position are permitted, as the . ;::
~; coupling cones can freely take position relative to the outer part of the coupling due to a cardan joint that improves the contact between ~he coupling surfaces and consequently improves the torque transfer capacity.
Some eccentrity is also permitted as the bearing func-tions only as an axial bearing supporting the weight of inner parts of the coupling and the shaft when the coupling is disengaged.
;~
This bearing permits some radial movement. Hence the coupling cones can be centered relative to the outer parts of the coupling.
-:; .,.
As the coupling operates in horizontal position, the bearing ~` carries the radial loads caused by the inner parts of the coupling. ` `
~ , . , The bearing also prevents the coupling cones from touching the ~" outer parts of the coupling when the coupling is disengaged. i .
The coupling cones can be more easily made take position ;
; by means of cup springs than by means of helical springs. Space " can also be saved with using cup springs.
: : - ;, The coupling is functionally a dry type coupling, but -"~ when using hydraulic oil as the pressurizing agent for engaging ~` the coupling, advantages of a wet-type coupling can also be '.::
; - 2 - - ;;i `
~z~9 :
achieved, as coupling surfaces can be cleaned with the same oil by rinsing unfavourable impurities accumulated on the surfaces due to the centrifugal force. The cleaning of the coupling surfaces can be further improved by fitting the coupling cones with grooves.
; The cardan joint construction belonging to a coupling in accordance with the invention considerably reduces the amount . of impurities caused by wear.
The position of the coupling can also be freely chosen as it operates equally faultlessly in vertical and horizontal pOSitions and in all intermediate positions.
In order to avoid seizure, for instance bronze cast iron should preferably be sele~ted as the material of the coupling surfaces.
` A coupling in accordance with the invention can be made ~;
to operate as an overlaod protection clutch by limlting the maxi-mum pressure of the oil that engages the coupling by means of a system external to the coupling.
A coupling in accordance with the invention can favour--ably be positioned between two shaft ends or in such a way that both input and output shaft leave the coupling coaxially to the same direction.
The invention will now be described in more detail by way of example only, with reference to the accompanying drawings in which~
Figure 1 is a schematic illustration of a friction . ~ .
coupling in accordance with the invention, installed in the drive `
mechanism of a ship;
Figure 2 shows a cross sectional view of a coupling in accordance with the invention; and Figure 3 is an exploded view of the coupling shown in . ~
figure 2. ~ ~
. .:
The drive mechanism of the ship illustrated in fig. 1 .~
.
, comprises transmission equipment by means of which engine 36 drives propeiler 30. Starting from engine 36, the equipment comprises cardan shaft 33 that drives V-belt pulley 32. V-belt pulley 32 is connected with V-belts 31 to V-belt pulley 35 of the drive mechanism which V-belt pulley 35 drives bevel gear 25. Tubular shaft 24 is supported with bearings on frame 38 of the drive mech-anism and is equipped with bevel gear 26 driven by gear 25. At its top end, tubular shaft 24 is connected with outer parts 2 and 3 of the couble-cone coupling. The inner parts of the coupling ` 10 are connected by means of shaft 1, passing through tubular shaft ~;~
24, with bevel gear 27 which, via bevel gear 28 and its shaft 29 drives propeller 30 of the ship. The bottom part of the frame of drive mechanism 38 is made pivotable in the direction of arrow B
for steering the ship. ;
Figures 2 and 3 illustrate the detailed construction of ` the double-cone friction coupling.
Outer part 2,3 of the coupling is arranged to rotate within capsule 37 as engine 36 rotates. The inner parts of the ;;
coupling comprise a cardan joint 4 fastened to the top end of ` 20 shaft 1. Cardan joint 4 is fastened to the shaft by means of conical sleeve 5 and bolts 17. Cardan joint 4 also comprises pins 8, of which there are four located perpendicularly and radi- ~ -ally as shown in fig. 3. Over the pins 8 are slides 7 of square `~
cross-section. On both sides of a slide there are annular pistons 14 and 15 with forks 14' resp. 15', into which slides 7 of pins 8 ~' fit. The top annular piston 14 is loaded from above by two oppo-site cup springs 9, supported at their inner edges by means of ring 10. The bottom annular piston 15 is loaded by two opposite ;~
:` cup springs 11 supported by means of ring 10. In the inner circum- `
` 30 ference of annular pistons 14,15 there is a groove for O-ring 22 that seals the inside of annular pistons 14,15 against the . ~ .
cylindrical surface of part 4.
'~:
' ; , `'`'`
z~z~
The coupling comprises two opposite coupling cones 12 and 13. Cone 12 is fastened with bolts 19 to annular piston 15 and cone 13 is fastened with bolts 19 to annular piston 14.
; Between annular pistons 14 and 15 there is a space into which pressurized agent, preferably oil, can enter through channels 6 in shaft 1. Shaft l is supported by a special bearing 21 relative to outer part 2 of the coupling.
A feature of the bearing 21 is that it only works as an axial bearing carrying the weight of the inner parts of the coupling and the shaft when the coupling is disengaged. Bearing 21 however permits a radial or tilting movement of the shaft l.
As the coupling is disengaged, bearing 21 centers parts 3,13 and
2,12 so to make coupling surfaces Sl and S2 stay apart. Cup springs 9 and ll provide the disengaging force.
Bearing 21 permits a movement in the direction of the radius of shaft 21 as the fit between shaft l and the inner ring of bearing 21, on one hand, and between outer part 2 of the coupling and the outer ring of the coupling, on the other hand is made looser than usual. Rotation of the inner and outer rings ` 20 of bearing 21 is prevented with stop pins.
The coupling described above functions as follows. As pressurized agent is supplied from pressurized source 40 through pipe 41 and channels 6 into the space between annular pistons 14 and 15, this agent urges annular pistons 14 and 15 in the direc-tion of arrows A, i.e. in the direction of the axis of shaft l, apart from each other which makes the outer surfaces of bevel " coupling elements 12 and 13 engage the inner surfaces of rotating parts 2 and 3. The coupling surfaces Sl and S2 therefore engage and the shaft l rotates along with outer parts 2,3 of the coupling.
As-the pressure is released from the space between annular pistons "~ 14 and 15, cup springs 9 and ll return the coupling to the dis-engaged position.
~, '.
.. ~ , . , ,.;
l~ZlZ~9 Cup springs 9 and ll are particularly advantageous as they make coupling cones 12 and 13 take up their position more evenly. The space requirement of cup springs 9 and 11 is also considerably lower that than of other spring types; they also make the construction simpler. ;
For the prevention of seizure, the material of the coupling surfaces Sl and S2 may be for instance, bronze cast iron.
Coupling parts 12 and 13 have grooves 12' and 13' for improved cleaning-up.
In association with pressurized agent equipment 40 there should preferably be means for limiting the maximum pressure of ; `-the engaging agent to a certain level in order to protect the transmission unit agains-t overload. ; , According to a preferred embodiment of the in~ention, in association of outer part 2,3 of the coupling, there is/are oil drain hole(s)~so to provide some lubrication on surfaces S and S
1 2 ~;
; for cleaning-up, even though the coupling is structurally of the dry type. ~, In the construction described above the input and output shafts leave the coupling on the same side thereof. The invention ~
can also be applied to such transmissions in which a coupling is `
arranged between the ends of adjacent shafts so that the shafts ~.
leave the coupling on opposlte sides thereof. ~ ~
:: ~.;
; ;
, ~ , , " , ; . . ...
Bearing 21 permits a movement in the direction of the radius of shaft 21 as the fit between shaft l and the inner ring of bearing 21, on one hand, and between outer part 2 of the coupling and the outer ring of the coupling, on the other hand is made looser than usual. Rotation of the inner and outer rings ` 20 of bearing 21 is prevented with stop pins.
The coupling described above functions as follows. As pressurized agent is supplied from pressurized source 40 through pipe 41 and channels 6 into the space between annular pistons 14 and 15, this agent urges annular pistons 14 and 15 in the direc-tion of arrows A, i.e. in the direction of the axis of shaft l, apart from each other which makes the outer surfaces of bevel " coupling elements 12 and 13 engage the inner surfaces of rotating parts 2 and 3. The coupling surfaces Sl and S2 therefore engage and the shaft l rotates along with outer parts 2,3 of the coupling.
As-the pressure is released from the space between annular pistons "~ 14 and 15, cup springs 9 and ll return the coupling to the dis-engaged position.
~, '.
.. ~ , . , ,.;
l~ZlZ~9 Cup springs 9 and ll are particularly advantageous as they make coupling cones 12 and 13 take up their position more evenly. The space requirement of cup springs 9 and 11 is also considerably lower that than of other spring types; they also make the construction simpler. ;
For the prevention of seizure, the material of the coupling surfaces Sl and S2 may be for instance, bronze cast iron.
Coupling parts 12 and 13 have grooves 12' and 13' for improved cleaning-up.
In association with pressurized agent equipment 40 there should preferably be means for limiting the maximum pressure of ; `-the engaging agent to a certain level in order to protect the transmission unit agains-t overload. ; , According to a preferred embodiment of the in~ention, in association of outer part 2,3 of the coupling, there is/are oil drain hole(s)~so to provide some lubrication on surfaces S and S
1 2 ~;
; for cleaning-up, even though the coupling is structurally of the dry type. ~, In the construction described above the input and output shafts leave the coupling on the same side thereof. The invention ~
can also be applied to such transmissions in which a coupling is `
arranged between the ends of adjacent shafts so that the shafts ~.
leave the coupling on opposlte sides thereof. ~ ~
:: ~.;
; ;
, ~ , , " , ; . . ...
Claims (9)
PROPERTY OR PRIVILEGE IS CLAIMED ARE DEFINED AS FOLLOWS:
1. A double-cone bevel coupling comprising a drive member provided with inner conical friction surfaces, an output shaft extending generally co-axially within said drive member, conical friction elements within said drive member having friction surfaces facing said inner conical friction surfaces of said drive member, annular pistons arranged generally concentrically with said output shaft and defining a space therebetween, said annular pistons being coupled to said output shaft by pivotal connections which allow the planes of said annular pistons to tilt relative to said shaft while being constrained to rotate therewith, said annular pistons being arranged to urge said friction elements into engagement with the drive member when pressurizing agent is introduced into said space, and said output shaft being supported relative to said drive member by means of a bearing allowing tilting of the shaft relative thereto, whereby in the event of angular deviations of the output shaft the annular pistons can tilt so that they remain correctly positioned in said drive member.
2. A coupling according to claim 1 wherein said pivotal interconnection comprise pins extending radially from said shaft, and forks on said annular pistons adapted to co-operate therewith.
3. A coupling according to claim 2 wherein said forks are fitted over sleeves arranged on said pins.
4. A coupling according to claim 2 having four said pins located uniformly around the periphery of said shaft, an upper said annular piston co-operating with a first opposite pair of said pins and a lower said annular piston co-operating with a lower opposite pair of said pins.
5. A coupling in accordance with claim 1, wherein cup springs are arranged outside the annular pistons bias the coupling into the disengaged position and center the friction elements.
6. A coupling in accordance with claim 1 wherein grooves are formed in the outer surface of the friction elements to clean the coupling surfaces.
7. A coupling according to claim 6 wherein said grooves are radial.
8. A coupling in accordance with claim 1 wherein for cleaning purposes, a hole, holes or a loose fit of the outer part is provided to allow some pressurized agent by means of which the coupling is engaged to flow over the coupling surfaces.
9. A coupling in accordance with claim 1 further comprising external pressure limiting means for the protection of the coupling against overload.
Applications Claiming Priority (2)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| FI790868A FI58543C (en) | 1979-03-14 | 1979-03-14 | FRIKTIONSKOPPLING MED DUBBEL KONA I SYNNERHET FOER DRIVANORDNINGAR FOER FARTYG |
| FI790868 | 1979-03-14 |
Publications (1)
| Publication Number | Publication Date |
|---|---|
| CA1121289A true CA1121289A (en) | 1982-04-06 |
Family
ID=8512486
Family Applications (1)
| Application Number | Title | Priority Date | Filing Date |
|---|---|---|---|
| CA000347645A Expired CA1121289A (en) | 1979-03-14 | 1980-03-14 | Friction bevel coupling with double cones particularly for use in drive mechanisms of ships |
Country Status (10)
| Country | Link |
|---|---|
| US (1) | US4318463A (en) |
| JP (1) | JPS55126128A (en) |
| CA (1) | CA1121289A (en) |
| DE (1) | DE3009085A1 (en) |
| FI (1) | FI58543C (en) |
| FR (1) | FR2451506A1 (en) |
| GB (1) | GB2044372B (en) |
| NL (1) | NL8001247A (en) |
| NO (1) | NO149437C (en) |
| SE (1) | SE444471B (en) |
Families Citing this family (5)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| DE3332785A1 (en) * | 1983-09-10 | 1985-03-28 | J.M. Voith Gmbh, 7920 Heidenheim | ELASTIC STORAGE OF A CYCLLOIDAL PROPELLER |
| DE3600196C2 (en) * | 1986-01-07 | 1999-04-01 | Udo Adam Gmbh Maschinenfabrik | Safety clutch |
| EP0321873B1 (en) * | 1987-12-19 | 1994-08-03 | GETRAG Getriebe- und Zahnradfabrik Hermann Hagenmeyer GmbH & Cie | Dual clutch transmission and its adjustment method |
| FR2706957B1 (en) * | 1993-06-24 | 1995-09-01 | Concone Edmond | |
| DE102018119199A1 (en) * | 2018-08-07 | 2020-02-13 | Hoerbiger Antriebstechnik Holding Gmbh | Powertrain of an electrically powered vehicle and electrically powered vehicle |
Family Cites Families (4)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| US1524231A (en) * | 1923-06-09 | 1925-01-27 | Siegfried Rosenzweig | Friction clutch |
| US1665076A (en) * | 1925-12-17 | 1928-04-03 | Tessky Karl | Friction disk clutch |
| US2386478A (en) * | 1943-06-23 | 1945-10-09 | Gen Tire & Rubber Co | Torque transmitting connection |
| AT296696B (en) * | 1968-01-27 | 1972-02-25 | Joern Gmbh | Switchable shaft coupling |
-
1979
- 1979-03-14 FI FI790868A patent/FI58543C/en not_active IP Right Cessation
-
1980
- 1980-02-29 NL NL8001247A patent/NL8001247A/en not_active Application Discontinuation
- 1980-03-07 GB GB8007840A patent/GB2044372B/en not_active Expired
- 1980-03-10 DE DE19803009085 patent/DE3009085A1/en not_active Withdrawn
- 1980-03-13 US US06/129,900 patent/US4318463A/en not_active Expired - Lifetime
- 1980-03-13 SE SE8001979A patent/SE444471B/en unknown
- 1980-03-13 NO NO800728A patent/NO149437C/en unknown
- 1980-03-14 FR FR8005841A patent/FR2451506A1/en active Granted
- 1980-03-14 CA CA000347645A patent/CA1121289A/en not_active Expired
- 1980-03-14 JP JP3258180A patent/JPS55126128A/en active Pending
Also Published As
| Publication number | Publication date |
|---|---|
| FR2451506A1 (en) | 1980-10-10 |
| NO149437C (en) | 1984-04-25 |
| US4318463A (en) | 1982-03-09 |
| JPS55126128A (en) | 1980-09-29 |
| DE3009085A1 (en) | 1980-10-09 |
| NO800728L (en) | 1980-09-15 |
| FI790868A (en) | 1980-09-15 |
| NL8001247A (en) | 1980-09-16 |
| SE8001979L (en) | 1980-09-15 |
| GB2044372A (en) | 1980-10-15 |
| NO149437B (en) | 1984-01-09 |
| GB2044372B (en) | 1983-05-25 |
| FI58543C (en) | 1981-02-10 |
| SE444471B (en) | 1986-04-14 |
| FI58543B (en) | 1980-10-31 |
| FR2451506B3 (en) | 1982-01-22 |
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Legal Events
| Date | Code | Title | Description |
|---|---|---|---|
| MKEX | Expiry |